Feed mechanism



A. J. KAYE FEED MECHANISM Nov. 22, 1960 Filed Deo. 30, 1958- Nov. 22,1960 A. J. KAYE 2,961,138

FEED MECHANISM Filed Dec. 30, 1958 3 Sheets-Sheet 2 A. J. KAYE FEEDMECHANISM Nov. 22, 1960 3 Sheets-5heet 3 Filed Dec. 30, 1958 UnitedStates Patent FEED MECHANISM Anthony J. Kaye, Schenectady, N.Y.,assignor to General Electric Company, a corporation of New York FiledDec. 30, 1958, Ser. No. 783,878 12 Claims. (Cl. 226-172) This inventionrelates to a stock feed mechanism for a punch press or the like, and inparticular, to a mechanism which is capable of high feed speeds andgreat accuracy in positioning the stock.

In feeding a punch press or similar device, the stock must be repeatedlypositioned in the work area of the press both at high speed and withgreat accuracy so that the various press operations may be carried outeffectively. lPresent day stock feed mechanisms such as roll and hitchtypes have not been entirely satisfactory, primarily because they arerelatively slow and inaccurate. Fundamentally all of these prior artdevices fail to clamp the stock continuously and, as a result, atvarious times the stock floats (i.e., is not positively gripped). Hence,the momentum of the stock moves it past the desired location in the workarea introducing positioning errors which result in spoilage and Wasteof the stock and excessive wear of the dies.

To overcome this problem, attempts have been made to eliminate stockoverride by feeding short of the work area, releasing the stock and thenaligning it properly by means of pilot pins located on the die. 'Ihissolution, however, has proved far from effective since it is apparentthat clamping and unclamping of the stock prior to final alignment ofitself introduces positioning errors. Concurrently, it also reduces, byvirtue of the need for final alignment, the speed with which the pressoperates. In addition to the economic losses due to slow and inefficientpress operating speeds, die costs are also increased since pilot pins orsimilar aligning instrumentalities must be incorporated in the dies tofacilitate the nal aligning operation.

In order to overcome the foregoing difculties and provide a feedmechanism which is both accurate and rapid in its operation, it iscontemplated to construct a feed mechanism wherein the material fed tothe press is positively clamped during the entire operation.

Therefore, it is an object of this invention to provide a feed mechanismwherein material being fed to an apparatus is continuously clamped;

Another object of this invention is to provide a feed mechanism in whichthe material is continuously clamped and there is no relative motionbetween the material and the clamping and advancing means;

Yet another object of this invention is to provide a feed mechanismwhich accurately positions the material in the work area of the punchpress without the use of pilot pins for aligning the material;

Still another object of this invention is to provide an intermittenthigh speed feed mechanism for a punch press or the like in which thematerial may be accurately positioned in the press work area byeliminating inertia override effects.

Other objects and advantages of the invention will become apparent asthe description thereof proceeds.

`In one embodiment the advantages of the invention are realized byproviding a feed mechanism having a multiplicity of clamping stationswhich are so actuated that each of the clamping stations in turn gripsthe stock and continues to do so until the succeeding clamping stationis brought into engagement with and grips the stock. Hence, a continuousclamping overlap is maintained between suscceeding clamping stations andthe stock is prevented from floating The novel features which arebelieved to be characteristic of this invention are set forth withparticularity in the appended claims. The invention itself, however,both as to its organization and method of operation, together withfurther objects and advantages thereof, may be best understood byreference to the following description taken in connection with theaccompanying drawings in which;

Figure 1 is a perspective view of the novel feed mechanism shown inconjunction with a punch press;

Figure 2 is a detailed side elevational View, partially broken away, ofone of the feed mechanisms illustrated in Figure l;

Figure 3 is a plan view of one of the feed mechanisms of Figure l;

:Figure 4 is a sectional view taken along the line 4-4 of Figure 3;

Figure 5 is an enlarged sectional view taken along the lines 5- ofFigure 3;

Figures 6 and 7 are diagrammatic illustrations of the indexing barrelcam and are useful in explaining the operation of the device;

Figure 8 is a perspective view of an alternative embodiment of the feedmechanism;

Figure 9 is a fragmentary elevation of the feed mechanism illustrated inFigure 8;

Figure l0 is a sectional view taken along the lines lll- '19 of Figure8;

Figure ll is a fragmentary perspective of yet another embodiment of afeed mechanism;

Figure l2 is a sectional view taken along the lines 12--12 of Figure l1;

Figure 13 is an enlarged perspective of a clamping mechanism.

Referring now to the accompanying drawings in which like referencenumerals denote corresponding parts throughout the several views, Figurel discloses a punch press indicated generally at 1 and having a frame 2which supports a press bolster section 3. A plate 4 is fastened to thebolster section 3 and supports similar feed mechanisms 5 and 6 formoving an elongated strip of material 7 from left to right to the presswork area, indicated generally at 8, where a die member 9 secured to areciprocating cam 10, carries out the desired operations.

The feed mechanisms 5 and 6 are identical in construction and operationand the subsequent discussion Will be limited to a description of themechanism 5 located to the left of the press. It will be understood,however, that the discussion applies with equal force to thecorresponding mechanism 6. The stock feed mechanism 5 is so constructedand arranged that as any increment of the stock 7 enters the feedmechanism it is clamped and advanced towards the press 1, remaining soclamped until a succeeding increment of the stock has passed into thefeed mechanism and is clamped thereby. To achieve the foregoing, thestock 7 passes between two plates 11 and 12 which are free to rotate ona common shaft 13. The plates support a multiplicity of spaced clampingstations 14, 1S, 16, 17, 18, and 19 which clamp the stock and advance ittoward the work area 8 of the press.

Each of the clamping stations includes a movable member 14a, 15a, etc.,secured to the upper plate 11 as may be seen most clearly in Figure 2,and a cooperating xed member 14b, 15b, etc., secured to the lower plate12. The movable clamp members are depressed, in Y Patented Nov. 22, 1960a manner presently to be described, and cooperate with their respectivefixed clamp member 14b, 15b, etc., to engage and clamp the stock 7. Thefixed clamp members have projecting pins or lugs extending below theplate 12 which are driven to rotate the plates 11 and 12 and advance theclamping stations and the material toward the work area 8 of the press.

' Positioned in the path of the clamping stations etc., and extendingparallel to the direction of movement of the stoclzsN a stationary camsurface 20 fastened to' an L-shaped mounting bracket 21 which locks theclamping stations intorclam'ping relation with the stock. Uponcounterclockwise rotation of the plates 11 and 12 each ofthe movable'clamp members 14a-19a successively passes underneath the cam 2t) whichurges them down to grip thestock 7, clamping it securely.

As can be seen most clearly in Figures 2 and 4, which shows clampingstation 17 beneath the cam surface 29, the movable clamp member 17a isurged downward into engagement with the stock 7. Upon rotation of theplate members 11 and 12 the clamping station 17 remains beneath andcontinues moving to the right of cam 2i) advancing the stock in the samedirection and remaining in clamping relation therewith during its entirepassage beneath the cam..

The spacing of the clamping stations aroundthe periphery of the platesand the length of the cam is such that each individual station 14-19 inturn passes beneath the cam and remains in contact therewith until thesucceeding station clamps the stock 7. Thus, the stock is continuouslymaintained in a clamped condition due to the overlap in clamping betweensuccessive clamping stations. Since the clamping stations move alongwith stock as it passes through the feed mechanism, there is no relativemotion between the stock and the `stations eliminating inertia effectsupon releasing the stocx.

In yorder to advance the material a predetermined amount with eachoperation of the press, a motion transmitting means is provided toactuate the feed mechanism by rotating the plates 11 and 12 in responseto each operational cycle of the press 1. A crank shaft fastened to thepress eccentric, not shown, is secured to a connecting rod 22, the lowerend of which is threaded and supported in `a rod end 23. The rod end 23is provided with a pin 25 which supports a crank arm 26 mounted on ashaft 27. The rod 22 is reciprocated with each operation of the camrotating, crank arm 26 and the shaft 27 during each press operation by apredetermined amount. The shaft 27, which is journaled in a suitablebea-ring mounted in bearing block 28, drives gears 3i) and 31 through aone way clutch 29 to transmit rotation in one direction only. Hence, theshaft 27 and the gears 30 and 31 are driven during the press upstrokeonly to rotate a barrel cam 32 mounted on a common shaft with the gear31, a predetermined amounty during each press operation.

The barrel cam 32 is so positioned that a helical groove 34 along thesurface of barrel cam 32 intercepts the pins 14b, 15b, etc., to advancethem a predetermined distance along the groove with each rotation of thebarrel cam. As the pins move along the groove 34 the plates 11 and 12are rotated` moving the individual clamping stations along beneath thecam member 20, and advancing the stock toward the press. To insure thatthe clamping stations move linearly while beneath the stationary cam 20,movement of the pins 141)',V 15b, etc., along the helical ygroove of thebarrel cam 32 is restricted by a pair of cam surfaces 35 and 36 (whichmay be seen most clearly in Figures 6 and 7) disposed directly above thecam 32 and form a linear guide which forces the pins to advance linearlywhile traversing the groove 34.

'However,` since the index pins are fixed to the plate 12 and tend tomove in an arc with rotation of plate 12,

the center of the-rotating plates 11 and 12 must be free to oscillate ifthe pins are to move linearly between the cams 35 and 36. Hence, theshaft 13 supporting the plates 11 and 12 is mounted on an arm 37 whichis free to pivot about a pin 38 secured in a bracket 39 fastened to thepress frame. The shaft 13 is journaled in the ball bearings 42 and 43fixed to the pivot arm 37 to permit the plates, which are fastenedtogether by bolts 41, to rotate about the shaft. A groove 40 in the arm37 forms a passageway to permit the index pins to pass during eachcomplete rotationof the plates 11 and 12.

The manner in which the shaft 13 oscillates as the pins move between thecams 35 and 36 is illustrated schematically in Figures 6 and 7. Thus, inFigure 6 the indexing pin 18b of clamping station 18 is Vshownapproximately midway down the linear path defined by the cams 35 and 36`while the indexing pin 17b of the succeeding clamping station isapproaching the left hand end of the barrel cani. With the shaft 13located as shown, the indexing pins 18h and 17b tend toV move along thearcuate path indicated in the drawing by the legend are If the shaft 13remains fixed, it is apparent from the drawing that no further. movementof the pin is possible since further rotation of the plates forces thepin against cam 35 preventing further'rotation of the barrel cam 32.

Consequently, the shaft 13 must vmove downwardly towards the cams untilthe chordal distance between the pins lies along the guide way, as shownin Figure 7, by the line bearing the legend chord, and the pins iarefree to travel linearly. Since the pivot arm 37 is free to move,continued rotation of barrel cam 32V and the action of pin 18b lon cam36, pulls `arm' 37 down, displacing shaft 13 as illustrated in Figure 7,until the chordal distance between Vthe pins llies :along the guideVway. -Thus, the pin 18h travels to the end of the passage 'and pin 17bis aligned with the opening between-the two cam plates 35 and 36. Thecenter of the rotating plates 11 and 12 oscillates in ythe manner sothat the indexing pins, the clamping stations and the stock 7 areadvanced linearly by the feed mechanism toward the work area.

The lstructural ydetails of the clamping stations are illus trated inFigure 5. The movable upper kclamp member 15a of station15 includes acylindricalmernber 44 having a tiange 45 which engages the underside ofplate 11. A

ball thrust bearing 4.6 having a iContact surface 47 is secured to thelower vend of the cylinder 44 and clamps the stock 7 against acooperating lower clamp member 15b whenever the cylinder 44 is displaceddownwardly. A cap 48 retaining aball 49 is threaded on the upper end ofthe cylinder 44, so that the ball49 makes contact with the stationarycam member 20 forcing the cylinder 44 down against the action of acompression spring member 50 fastened between the cap and the surface ofthe plate 11.

The lower clamping member`15b also includes a bali thrust bearing "51Vhaving a contacti surface 52 which cooperates with the correspondingsurface 47 of the movable clamping member to hold the stock 7 Anindexing pin or 1ug53 is rigidly fixed to the plate 12 by means of a setscrew 54 and extends'below the plate 12 to engage the groove 34 inv theVbarrel cam 32. Ball thrust hearings 46 and 51 are provided-so thattheContact surfacest47 and 52 will not rotate with respect lto the stock 7as plates 11 and 12 turn about shaft 13.l VThat is, 'as plates 11 and 12'rotate about the shaft 13, carrying the clamping stations with it, thestations tend torotate about their own axes. Any such rotation, ortendencyto rotation, of the clamping stations will produce acorresponding rotation or tendency to Vshifty the'stocl; `7 out ofvalignment. The thrust ball bearings 46 and 51, however, permit theclamp-ing stations to rotate about a vertical axis relative to theplates 11 and 12 so that contact surfaces 47 and 52 which grip the stockwill not rotate with respect to the stock. Consequently, anypdanger ofmisaligning Ythe material due to rotational movement of the plates andthe clamping stations is eliminated.

In operation, the reciprocating rod 22 driven by the press eccentricrotates the barrel cam 32 on each press upstroke through the one-wayclutch 29. The index pin 18]: located on clamping station 18 has comeinto alignment with the groove 34 and moves into the groove and betweencams 35 and 36, as barrel cam 32 rotates. Movement of the pin into thegroove 34 rotates the plates 11 and 12 about shaft 13 bringing themovable upper clamping jaw 18a under the stationary cam member 20 urgingit downward to grip the stock 7. Since the path of the index pin iscaptured between the cams 35 and 36, further rotation of the barrel camadvances the clamping station underneath the cam 20 moving pivot arm 37to facilitate linear motion of the clamping station.

As the clamping station 18 continues to move towards the right andapproaches the end of the stationary cam 20 the index pin 17b of thesucceeding clamping station 17 moves into the barrel cam groove andbrings station 17 under the fixed cam 20, clamping the next portion ofthe stock before station 18 moves out from underneath the cam 20. Thus,the stock 7 remains continuously clamped and never floats since thesucceeding clamping station has clamped the material before thepreceding clamping station is released. On the next press upstroke thesucceeding clamping station moves linearly underneath the fixed cam 20and the sequence of operation is repeated to continue supplying stock tothe work area of the press 1.

It is obvious from the description of the invention that the feedmechanism 5 may be adjusted to advance the stock any desired amountduring each press upstroke by varying the length of the rod 22 and theangle of the crank arm 26. Furthermore, the ratio of gears 39 and 31 maybe adjusted to control the rotation of lthe barrel cam 32 and vary thedegree the stock advances during each upstroke of the press.

As shown in Figure 8, the stock may be clamped and advanced -byutilizing continuous belts 'above and below the stock to perform thesame function as the plates 11 and 12,. Thus, a pair of endless metallicbelts 60 and 61 positioned above and below the stock support amultiplicity of upper plates 62a, 63a, 64a, 65a, 66a, 67a andcorresponding lower plates 62b, 63b, etc., which, upon rotation of thebelts 60 and 61, brings successive ones of the clamping plate pairs intoengagement with the stock 7 to advance it from left to right towards thepress working area, not shown. A pair of cam surfaces 69 and 7?, as seenclearly in Figure 10, 7are supported by a bracket 71 and bring theclamping plates into engagement with the stock 7 and advance it towardsthe press.

Motion is transmitted from the press to the belts 60 and 61 to advancethe stock a predetermined amount with each press operation. Theconnecting rod 22, which as described with reference to Figure 1, isconnected to the press eccentric, is reciprocated in synchronism witheach press upstroke to rotate a crank arm 26 and a shaft 27 to which itis fixed through the one way clutch 29. Rotation of shaft 27 drivesbevel gears 75 to transmit motion to gears 77 and 78 which drive belt 61in a clockwise direction. A pair of idler gears 79, only one of which isshown, are mounted on a shaft 82 and are driven by the belt 61.

A gear 80, mounted on the shaft 76, is also driven from the shaft 27 andmeshes with a gear 81 to drive a shaft 83 to which it is secured. Theshaft 83 supports gears 84 and 85 which drive the belt 60 in acounterclockwise direction. A pair of idler gears 86, only one of whichis shown, are secured to a shaft 87 and are driven by the belt 60. Thebelts 6) and 61 and the clamping plates which they support are rotatedto advance each of these clamping plates underneath cam members 69 and70, urging them into contact with the stock 7 to advance it towards thework area of the press. As can be seen most clearly in Figure 9, the

spacing between the clamping plates 62a etc., is such that amultiplicity of the clamping plates are simultaneously under the cams 69and 70 and there is a continuous clamping overlap between successiveones of the plates, and the material 7 is firmly and positively clampedat all times.

Each of the upper clamping plate members 62a, etc., as may be seen mostclearly in Figure 13, includes a stem 110 which is slidably mounted in acap 111 secured to a rod 112. A pin 113 fastened to the stem 110 is freeto move in slots 114 in the cap 111 to permit downward movement of thecap when the rod 112 passes beneath the cam 69 to compress a pair ofdisc springs 115 positioned between the cap 111 and the belt 60. Thedisc springs 115 are of Well-known construction and include a pair ofround tapered discs having a central passage for the stem 110. Thesprings act as pressure springs which are compressed by the action ofthe cam 69 and the cap 111 to urge the clamping plates 62a, 63a, etc.,into engagement with the stock.

Referring now to Figure 11, there is illustrated yet another embodimentwhich, though similar to that illustrated in' Figure 8, differstherefrom by the elimination of the continuous supporting belts 60 and61. Thus, in the arrangement of Figure 11 a link chain 90 and a sprocketwheel 91 is actuated in a similar manner to that illustrated in Figure 8to advance a multiplicity of clamping plates 92a, 93a, 94a, and 95asecured to the individual links of the chain into clamping position withthe stock to be fed to the press. Although, for simplicity ofillustration, only one chain link is illustrated in Figure 1l, it willbe understood by those skilled in the art, that corresponding chainlink, not shown, supports the other left-hand ends of the plates 92a,93a, etc. Similarly, a corresponding chain drive arrangement, as may beseen in Figure 12, is positioned beneath the stock to facilitateclamping.

Each of the plates 92a etc., includes a stern 1x10 which slides in a cap111 supporting a rod 112 which is adapted to pass underneath the cammember 69. The cap 111 contains vertical slots 114 which receive atransverse pin member 113 secured to the stem 110 which moves within theslot when the cap 111 is depressed during the course of its passageunderneath the cam 69. A disc spring assembly 115 is mounted between thebottom of the cap and the underside of the clamping plate and iscompressed by the downward movement of the cap 111 to maintain the platefirmly in engagement with the material.

The clamping plates 92a, 93a, etc., are supported on flanges 103.rigidly secured to the chain links of the chain 90. Fixed to each ofthe flanges 103 is a mounting pin 104 which extends through the plates92a, etc. As the rods 112 pass underneath the cam 69 compressing thesprings 115, the clamping plates slide along the pin 104, as may be seenmost clearly in Figure 12, until they engage with the stock 7. In thisfashion, the chain 90vis not' distorted as the plates engage the stockas they would if the plates were rigidly secured to the chain. A recessin the plates is adapted to receive the head of the pin 104 as the plateis moved into clamping position along the pins, thus presenting a smoothclamping surface to the stock 7. In this manner each of the individualclamping plates is secured to one of the links of the chain 90 and aresequentially brought into engagement with the stock without in any waydeflecting or distorting the driving chain.

While a particular embodiment of this invention has been shown, it will,of course be understood that it is not limited thereto since manymodifications both in the circuit arrangement and in theinstrumentalities employed may be made. It is contemplated by theappended claims to cover any such modications as fall within the truespirit and scope of this invention.

' Whaty I claim as new and desire.. to obtainfby Letters Patent of theUnited States is: Y v Y l. In a mechanism for feeding material toYanrapparatus, the combination comprising feed means foriadvancingmaterial toward the work area of the apparatus includY` ing amultiplicity of clamping means successivelyjengaging material enteringsaid feed means; motion-transmitting means to actuate said feed means'in;respons'e` to each operational cycle of the apparatusY includingmeans for contacting at least one of said' clamping means and. urging itinto engagement with'the material'andj'positively maintaining theclamping means in'engagem'ent with said material during each operationalcycleof said apparatus, each of said clamping means being fmaintained inengagement with said .material `until the. suc-x ceeding clamping meansengages ithe materialY so that it is continuously clamped while beingfed tothe apparatus.

2. In a mechanism for feeding material'toan apparatus for performingoperations' thereon, the lcombination comprising a rotary feedmeans'including a"multiplicity of clamping stations successive cones jofwhich :are adapted to engage and'advancetheqmaterial `upon`1rotajtion ofsaid feed means, motion transmitting'meansrifolr rotatably actuatingsaidrfeed means in response to each operational cycle of said apparatusand rotatingV succeeding ones of said stations into engagement :withAsaid material, said clamping stationsbeing so positioned and spacedthat the succeeding clamping station'engages the material before thepreceeding station releases saidY material so that the material iscontinuously `clampedwhile being fed to said apparatus.

3. In an intermittent feed mechanism for supplying an elongated materialto an intermittently'operated apparatus, the combination comprisingrotatable. plate means for supporting a multiplicity of. spaced clampingstations adapted to engage the material, contact `means to urge saidclamping stations into engagement .with said material, said contactmeansextending in the direction of motion of said material to maintain said'clamping stations in engagement with said material for a .predetermineddistance and motion' transmitting means to rotate .said plate means inresponse'to each operational cycle kof said apparatus to bring theclamping stations successively into interacting position. withgsaid'contact means to engage and advance said material during eachVrotation, said clamping'stations being'so'spaced'thateach stationremains in engagement with said material'until .the succeeding clampingstation is'brought into interacting position with said contact meanswhereby said material is clamped continuously by one 'of said stations.

4. In a mechanism for feeding material to an apparatus for performingoperations thereon the combination comprising a rotating feed meansincluding a multiplicity yof lspaced clamping stations adapted to bebrought successively into engagement with land toV advance-the materialto the operating area of said apparatus, Vcam means positioned in thepath of-said stations'extending in the direction of motion of saidmaterial, motion transmitting means to rotate said feed means from saidapparatus during each operational'cycle thereof to Vbring the clampingstations successively into'conta'ct withsaid cam surface causing them toengage and :advance .said material, said cam and said stations being soconstructed and shaped that succeeding clamping stationsare brought intocontact Ywith said cam means before the preceeding station loses contactwith said cam so that said material is always positively clamped by `oneof `said clamping stations.

5. In an intermittent feed mechanism for a reciprocating apparatus thecombination comprising a rotating feed mechanism including a pair ofspaced rotatable elements arranged lto have an elongated materialrpasstherebetween, atmultiplicity of spaced clamping `stations n mounted onsaid rotatable elements,rsaid clamping stations cooperating to engageand advance said material,

., arranged that each clamping station remains in contact with said cammeans at leastuntil the succeeding station comes in contact with saidcam means whereby the material is always clamped by one of saidstations.

6. In an intermittent material feed mechanism for a Yreciprocatingapparatus, the combination comprising a pair of spaced rotatable platesarranged to 'have the material passtherebetween, a multiplicity ofclamping stations mounted on said plates, each of said clamping stationscomprising a movable contact member extending through and projectingbeyond one of said plates and cooperating with a fixed member extendingthrough and projecting beyond said other plate, cam means positioned toengageY said movable contact and urge it into engagement with saidmaterialand said'xed member to clamp said material, intermittent motiontransmitting means engaging the projecting portions oftsaid fixedcontact members to rotate said plates during each reciprocation ofv saidapparatus and bring theY corresponding movable contact into engagementwith said cam means to clamp said material and advance it a givendistance during each reciprocation of said apparatus, said clampingstations being so spaced that each station remains in contact with saidcam means at leastuntil the succeeding station comes in contact withsaid cam means whereby the material is always clamped by one of saidstations.

7. In an intermittent feed mechanism, the combina- Vtion comprising feedmeans for advancing material towards a work area, said feed meansincluding a multiplicity of movable clamping means to engage successiveportions of the material, each of said clamping means including anindexing pin, intermittent motion transmitting means to actuate saidfeed means including cam means to engage index pins of the individualclamping means to advance said clamping means a predetermined amountduring each intermittent motion, and means to cause said clamping meansto engage andv remain in engagement with said material until thesucceeding clamping means engages said material whereby .the material iscontinuously clamped. Y

8. In an intermittent feed mechanismfor a press or the like, thecombination comprising feed means for advancing material toward the workarea of the press, said feed means including a multiplicity of movableclamping means including individual index pins to engage upon movementthereof successive portions of Vthe ymaterial,

Y motion transmitting means responsive to each operation of the press toactuate said feed means, said transmitting means including a barrel cammeans having a groove ,t member adapted to receive the index pins ofsaid clamping stations, the rotation of said barrel cam advancing saidclamping stations a predetermined amount'during each operational cycleof said apparatus, and means maintaining a given clamping meansinengagement ,-with .said material 'until the succeeding clamping meanshas been'brought'intoengagement withv saidtmaterial so thatsaid-material is continuously clamped while Abeingfed to said press.

v9. In an intermittent feed mechanisml for a press or the like, thecombination comprising alinear feed' means for advancing the material tothe workV area* of the press including a pair of rotating plates betweenlwhich said-material. is adapted to pass, amultiplicityof `spacedclampingstations positioned on saidrotatingplatemeans, suc- .cessiveones of which are adapted to engagethe material upon rotation of saidplate means, each of said clamping means including an indexing pinextending from said plate means, motion transmitting means responsive toeach reciprocation of said press to rotate said plate means and bringingsuccessive ones of the clamping means into engagement with saidmaterial, said motion transmitting means including a barrel cam having ahelical groove therein adapted to receive the indexing pin from theindividual clamping stations whereby rotation of said barrel camadvances said pin and the associated clamping means a predeterminedamount during each reciprocation of the press, and cam means positionedin the path of the clamping means and adapted to cause each of saidclamping means to engage said material upon being rotated into contacttherewith, said clamping means being so spaced that each clampingstation remains in contact with said cam means at least until thesucceeding clamping station is rotated into contact with said clampingmeans whereby said material s always clamped while fed to the press.

10. The intermittent feed mechanism of claim 9 including means toproduce linear motion of said material by causing said individualclamping means to move linearly while engaging said material.

11. The intermittent feed mechanism of claim 10 including cam means torestrain movement of said index pins in the groove of said barrel cam ina straight line.

12. The intermittent feed mechanism of claim 11 including pivotablemeans to support said rotating plate means whereby the center of saidrotatable plate means is permitted to oscillate.

References Cited in the file of this patent UNlTED STATES PATENTS977,146 Von Glahn Nov. 29, 1910 1,568,047 Bisey Jan. 5, 1926 1,765,419Goss June 24, 1959

